Steam trap



May 17, 1960 w. J. KINDERMAN STEAM TRAP 14 Sheets-Sheet 1 Filed Oct. 19, 1953 May 17, 1960 w. J. KINDERMAN V 2,936,772

swam TRAP Filed Oct. 19, 1955 14 Sheets-Sheet z 67 "I, A 66 A. 55

May 17, 1960 w. J. KINDERMAN 2,936,772

STEAM TRAP Filed Oct. 19, 1953 14 Sheets-Sheet 3 INVENTOR May 17, 1960 w. J. KINDERMAN 2,935,772

STEAM TRAP Filed Oct. 19, 1953 14 Sheets-Sheet 4 I /A v 55 AT TOR S May 17, 1960 w. J. KINDERMAN STEAM TRAP 1.4 Sheets-Sheet 6 Filed Oct; 19, 1953 & m

y ,1 w. J. KINDERMAN 2,936,772

' STEAM m? Filed Oct. 19, 1953 14 Sheets-Sheet '7 64 6? $2 I as r I INVENTOR May 17, 1960 v w. J. KINDERMAN 2,936,772

I STEAM TRAP Filed Oct. 19, 19s: 14 Sheets-Sheet a INVENTOR y 1960 w. J. KINDERMAN 2,936,772

STEAM TRAP Filed Oct. 19, 1953' 14 Sheets-Sheet 10 y ,1960 w. J. KINDERMAN 2,936,772

s'rsm TRAP ile Oct. 19, 1953 v 14 Sheets-Sheet n Hill/I NVENTOR May 17, 1960 w. J. KINDERMAN 2,

STEAM TRAP v Filed Oct. 19, 1953 I, 14 Sheets-Sheet 12 L3,) $imlllrlmlmum '1' III 52 1 95 7 3" I a??? r 70'), 701 *-I?. \\Q-Q 1/0 l 102 05 i ss 703' I0] lNVENToR y 17, 1950 w. J. KINDERMAN 2,936,772

STEAM TRAP Filed Oct. 19, 1953 V 14 Sheets-Sheet 13 INVENTOR May 17, 1960 w. J. KINDERMAN STEAM TRAP 14 Sheets-Sheet 14 Filed Oct. 19, 1953 w 55K wmtmg '97 19 a J Q INVENTOR W/M 75? J Kl/YDAEXWAM BY TTORNEYS Un ed Se 71 STEAM TRAP I Walter J. Kinderman, Philadelphia, Pa., assignor to Yarnall-Waring Company, ChestnutHill, Pa., a 'corporation of Pennsylvania Application October 19, 1953, Serial No. 386,883

as Claims. 01. 131-183 The present invention relates to the removal of condenstate from a steam space, and especially to steam traps forremoval of condensate. I

A purpose of the invention is to control the removal of condensate from a steam space in response to the pressure in the throat of a single orifice through which fluid A 2,936,772 Patente M 17, 59..

piece of a main valve on the inside controlling the, main; stream. f

A further purpose is to provide a groove on the tail piece located outside of the orifice when the valve is, closed and bring the groove into the orifice when the valve opens to change streamline flow to turbulent flow.

A further purpose is to provide a piston freely moving in a cylinder for the control chamber and to interconnect the orifice with the control chamber by a presSure'ta pQ A further purpose is to use a resilient wall on the control chamber such as a diaphragm or bellows to operate the valve and connect the interior 'of the control chamber to the orifice by a pressure tap.

A further purpose is to employ a disc valve forming one wall of the control chamber and to create the orifice by a recess along the disc, while the pressure tap extends transversely to the recess through the disc.

ment elfects when the main stream trap valve is open;

under conditions of streamline flow, and to regulate dis charge of a main stream from the space in response to pressure at that orifice, as distingished from the pressure beyond that orifice or between two orifices.

A further purpose is to selectively create conditions of streamline flow and conditions of turbulent flow in an orifice discharging from a space containing steam and condensate, and to control discharge of a mainstream in response to the transition from streamline flow to turbulent flow and vice versa. I

A further purpose is to control"theop'eration of' a steam trap by pressure closer to the temperature for saturated steam under the particular conditions than has been possible heretofore. i

A further purpose is to obtain-a snap action in steam trap operation in response-to pressure controlled by flow through an orifice. I

A further purpose is to pr steam trap.

A further purpose is to make a steam trap respond more quickly to variations in the character of the flow discharge. v d

A further purpose is to avoid abrupt changes in cross section of the flow stream precedingthe orifice and in the orifice so as to avoid the tendency to create thermo dynamic equilibrium and thereby prevent flashing of condensate. p I d V A further purpose is toemploy a curvature on the entrance surface or mouth of the orifice which will con-. form as closely as possible to the natural curvature of the flow stream so as to enter the restriction or throat with minimum turbulence. in practice an entrance radius between /2 the throat diameter and throat diameter serves to approximate the requirements for a round orifice.

A further purpose is toemploy a control orifice throat length not less than the throat diameter. and preferably not greater than ten times the'throat diameter.

A further purpose is to bring the curvature of the deflecting surface of the mouth of the orifice into .tangencywith the throat. i A further purpose is to the mouth of the orifice and 16 microinches. I A further purpose is. to extend the curvature outward to at least two-thirds the radius of curvature.

A further purpose is to create duce a more economical employ a surface finish on the throat which is less than the orifice mthe A further purpose is to dispose the control piston so that it will be relatively insensitive to accumulation of dirt from the medium. V L

' A further purpose is to minimize the velocity impinge- Further purposes appear in the specification andin the claims. I I In the drawings 1 have chosen to illustrate a few only of the numerous embodiments in which my invention may appear, selecting the forms shown from the standpoints of convenience in illustration, satisfactory operation and clear demonstration of the principles involved. Figure 1 is a vertical longitudinal section of a steam trap of the present invention in closed position, the section being taken on the line 1--1 of Figure 2.

" the variant trap in closed position.

Figure 2 is a vertical transverse section of Figure 1 on the line 2-2.

Figure3 is a top plan view of'the steam trap of Figures 1 and 2.

Figure 4 is a section corresponding to Figure l, but showingthe trap in open position.

Figures 5 and 6 illustrate a variant of the steam trap of the invention. 7 Figure '5 is a central longitudinal vertical section of Figure 6 is a view corresponding to Figure 5 showing the trap in open position.

Figures 7 and 8 illustrate a further variant of the trap of the invention in central vertical longitudinal sections,

'' Figure 7 being in closed position and Figure 8 in open position.

Figures 9 to 11 illustrate a still further variant of thesteam trap of the invention.

Figure 9 is a central vertical longitudinalsection show-- ing the trap in closed position.

ing the trap in open position.

ing the trap in open position.

- Figure 10 is a view corresponding to Figure 9 illustrat- Figure 11 is an enlarged fragmentary section on the line 11-11 of Figure 9.

A, further variant of the trap of the trated in Figures 12 to 14 inclusive. V

Figure 12 is a central vertical longitudinal section show: ing the variant trap in closed position.

Figure 13 is a fragmentary enlargement of of. Figure 12. d Figure 14 is a section corresponding to Figure-'12 shows invention is illus:

a [portion Figures 15 and 16 illustrate a further embodiment of the invention, with minor variations being illustrated in space between an. orifice ring on'the outside and a tail; ,7

Figures 17 to 17. Figure 15 is a central vertical longitudinal section show.- ing the variant steam trap in closed position,.whi1e-Figare 16 is a similar view showing the trap in open position;

- Figures 17 to 17c inclusive are fragmentary enlarge? 3 ments of the orifice of the trap of Figures and 16, with different forms of the pressure tap.

Figures 18 and 19 illustrate another embodiment of Figure 20 is a central vertical longitudinal section with the trap closed.

Figure 21 is a fragmentary enlargement of a portion of Figure 20.

Figure 22 is a section corresponding to Figure 20, but with the valve in open position.

Figure 23 is a fragmentary bottom plan view of the valve of Figure 20, with the seat shown in dot-and-dash lines for placement.

Figure 24 is a fragmentary enlarged section of Figure 23 on the line 2424.

Figure 25 is a fragmentary enlarged section 'of Figure 23 on the line 25-25.

Figure 26 is a fragmentary enlarged section corresponding to Figure 21 but showing a minor variation. A further embodiment of the invention is shown in Figures 27 and 28 in central vertical longitudinal sections,

Figure 27 showing the valve closed and Figure 28 showing the valve open.

Figures 29 and 30 are central vertical longitudinal sections'of a still further embodiment, Figure 29 showing the valve closed and Figure 30 showing the valve open.

Figures 31 and 32 are central vertical longitudinal sections of another form of the steam trap of the invention, the valve being closed in Figure 31 as far as it will close and being open in Figure 32.

Figure 31a is a fragmentary enlargement of Figure 31.

Figure 3112 is an enlarged fragmentary bottom plan of the valve of Figure 31.

- Figures 33 and 34 are central Vertical longitudinal sections of another form of the invention, the steam trap valve being closed in Figure 33 and open in Figure 34.

Figure 35 is a fragmentary section corresponding to Figure 33 showing a further variation.

Figures 36 and 37 illustrate in central vertical longitudinal sections another embodiment of the invention,

the valve being closed in Figure 36 and open in Figure 37. Figure 38 is a curve useful in explaining the invention.

Describing in illustration but not in limitation and referring to the drawings:

Steam traps have been widely used which are operated by the pressure in a control chamber which responds. to a characteristic or property of fluid flowing from the trap.

In the most widely used form of such prior art traps, fluid flows through two orifices in series, and the trap is operated by pressure variation between these two orifices. Traps of this character present a problem from the standpoint of manufacture because of the high tolerences re- '4 perature and vapor pressure drop to mits valve lift.

The present invention is designed particularly to produce a comparatively inexpensive steam trap which will operate very close to the temperature of saturated steam at the particular pressure, thus greatly reducing the lag which has existed in the prior art two orifice traps and in the prior art single orifice turbulent flow traps.

In accordance with the present invention, fluid, which may be steam, condensate, or a mixture of vapor and condensate, escapes from the closed space of the trap to the atmosphere or other point of discharge under condithe value which per- 7 tions of streamline flow, Streamline flow is very important in this connection as it permits maintaining a metastable state in the condensate, so that condensate which is under conditions of temperature and pressure I flash into vapor, but is actually liquid because of the streamline flow.

In order to secure the streamline flow in accordance with the invention, the deflecting surfaces of the mouth of the orifice must conform to special requirements of curvature corresponding to or approximating the natural curvature of the liquid flow stream in conforming to the throat restriction. It will be understood that if the stream 'is following a straight wall and encounters a shoulder or corner spaced from that wall to form an orifice, the

, approach to the desired benefits.

quired and the expensive materials which must be used, 5

Efforts have been made also to control the operation of a steam trap by fluid under equilibrium conditions induced by turbulent flow, and controlling'through a pressure tap from the turbulently flowing stream, as in Schott, U. S. Patent No. 2,234,387, granted March 11, 1941, for Steam Trap. The control pressure in this case is essentially vapor pressure. This has the disadvantage that the trap discharges at a comparatively low temperature compared with the temperature of saturated steam at the particular pressure. Therefore there is excessive .lag' in trap operation, and the trap continues with the trap valve remaining closed for a substantial time until the temshoulder or corner is the deflecting surface influencing the stream which must be controlled in curvature, and not the straight wall which is free from change in directional influence. V

In accordance with the invention, the curvature should be equal to the natural form of the flow of liquid entering a sharp edged orifice and flowing free but in practice an approximate entrance curvature between /2 the orifice diameter and the orifice diameter will result in reasonable It will of course be understood that if the orifice is not round but of some other configuration, the dimension which controls the curvature is the dimension normal to the wall at which the curvature exits on the side adjoining the orifice, that is, the distance across the orifice. It is most desirable that the surface curvature at the mouth be a smooth tangent to the throat at the inside of the orifice. This is however less necessary at the outside, and in fact the curvature extends out from the orifice at the mouth for a distance of two-thirds of the radius, thisv is sufficient. The zone of demarcation between the forward face of the throat wall and the mouth should be burnished or otherwise rounded to merge with the curvature. It. is important also that the orifice in streamline flow be free from circumferential grooves or scratches or other projections which will tend to promote turbulence, and with this end in view the entire orifice including the curved mouth and the throat should be burnished, polished or otherwise finished to obtain a surface finish of less than 16 micro inches.

In order that the conditions in the throat can .be effective for control purposes, the generally straight (it is sometimes made slightly diverging) portion of the throat of the orifice should have a length not less than the diameter at the throat. Where the diameter at the throat changes, this. should be the minimum diameter. This feature is important for the establishment of critical pres sure conditions for steam flow within the restriction of the orifice to insure a sufliciently high control pressure for valve closure Too short an orifice will permit expansion of the steam beyond the confines of the orifice before critical pressure conditions can be established,,thusperother configuration to take a-wrench or. other It has been found that excessive length of the throat is" not desirable and for ordinary purposes there is no advantage in employing a throat morethan ten times the diameter. I

-A pressure tap extends out from the throat generally transverse thereto and communicates with the control chamber to open and close the valve depending upon the conditions of flow in the throat. The angle of the pressure tap while generally transverse will where desired be varied to create changes in flow conditions between complete suppression of vapor pressure effects at the pressure tap and full vapor pressure effects. For example a very narrow slitted opening for the pressure tap with the length of the slit disposed normally to the direction of the stream in the orifice, has a large tap area but has small efiect on direction of flow, and so produces'minimum disturbances of'the flow stream per unit cross-sectional area of tap opening. Likewise by changing the location of the tap opening along the throat or varying the angle of the pressure tap with respect to the stream (while keeping the pressure tap generally transverse) varying amounts of vapor suppression will be obtained as desired.

In accordance with the invention, a snap action in opening' and closing of the trap valveis obtained which is not obtained with control by pressure between two orifices and is not obtained by control through turbulent flow through one orifice.

Considering first the form of Figures 1 to 4, the steam trap casing 50 has an inlet 51 suitably threaded or otherwise constructed to connect with piping and an outlet 52 likewise suitable threaded or otherwise provided for connection to piping. Between the inlet and outlet ex tends a cross wall 53 which has a main valve seat 54' preferably disposed with its axisvertical. In the form of Figures 1 to 4, and in a number of other forms, the main valve seat 54 is removable and threaded in the wall 53, whereas in other forms the main valve 54 is formed directly in the wall 53, either procedure being used where desiredl "Suitable passages are provided to connect the main valve seat with the inlet and outlet in the different forms;

vA bonnet 55 is threaded into an opening suitably at the top or bottom of the casing axially in line with the main valve seat, and the bonnet housing the control chamber in'the various forms being shaped 'as required in each embodiment. The bonnet is suitably of hexagonal or of tool :for removing and tightening the bonnet.

In the form of Figures 1 to 4,- valve 56 occupies the space'inside the bonnet and cooperates with the'valve seat to open and close a main stream of fluid flowing through the valve when the valve is open. In the form of Figures 1 to 4, the valve has a suitable conical surface 57 which engages the valve seat when'the valve is closed. At its end remote from the valve seat and inside the bonnet, the valve is outwardly flanged to form a piston 58 which makes a free sliding fit on the inside of cylinder 60 in; the bonnet. a v

The space inside the cylinder 60 between the end of the cylinder and the piston 58 forms a control chamber 61- which regulates the valve operation in response to pressure variations;

-Wholly separate from the valve and valve seat in the form of Figures 1 to 4, a single control orifice 62 communicates directly fromthe inlet to the outlet and passes a continuous stream of fluid. The control orifice 62 in this form is provided between anorifice ring 63 which is desirably mounted as'by threading in the cross wall 53 in' line with the axis of the valve and tail piece 64 extending axially from the valve through' the opening in the valve seat and through the orifice ring 63,, Thus the orifice is annular in shape. The deflecting surface of the orifice in the present instance is the shoulder of theorifice ring 63 and this is -filleted,,,or annularly curved'atj65 around the approach corner so as to favor streamline flow, the curvature being on a radius, between half the diameter and the diameter of the throat, in this case the radial dimension of the ring-orifice. The length of the throat of the orifice is also between-the diameter and ten times the diameter in this form.

Suitable passages are provided from the inlet to the orifice and from the orifice to the outlet.

Transversely to the direction of the stream flow throughthe orifice pressure taps 66 extend in this case radially inwardly and communicate with the control chamber, in

this instance through a passage 67 in the stem and a passage 68 in the valve beyond the main seat. The pressure tap should have a diameter not exceeding thethroat 7 These grooves tend to create turbulence when the valve opens and change from flow in metastable liquid equilibrium, favoring closing of the valve and overcoming any impact effect from the stream in holding the valve open. This avoids the necessity of using a reverse taper onthe control chamber, as has sometimes been employed.- Thus it willbe seen that in the form of Figures 1 to 4 the control orifice is in the center around the tail piece,- and the control orifice continuously discharges fluid, while the control tapping at right angles to the stream communicates the throat pressure to the control chamber.

When condensate of relatively low temperature; is flowing through the control orifice, a low pressure-is maintained in the pressure tap 66, lowering the pressure p The valve then opens and discharges the main stream of condensate through the space between the main valve and main valve seat. a i

When the temperature of condensate rises close to the temperature for saturated steam.-or when steam passes through the control orifice-'62, pressure in the pressure tap rises and increases the pressure in the control chamber, causing the valve to close. This closure is aided by the efl'ectof thegrooves70 which are brought into the orifice in open position of the valve creating a condition favorable to closing bycausing metastable condensate to flash. Thus a positive response is secured to close the valve. beneath the valve seat in maintaining the valve open. Of course when the valve is closed the tail piece grooves .are not in the path of the flow through the orifice and in metastable state and flashing is suppressed.

In the form of Figures 1 to 4 there is inevitably some leakage between the piston 58 and the cylinder 60. This leakage is small and by the construction of the invention is likely to be outward due to highercontrol chamber pressure especially when the valve is closed. This has a tendency to prevent an accumulation of dirt around the wall of cylinder 60 which might clog the construction. The location of the piston 58 at the top is also advantageous to prevent dirt from entering, although the valve will Work with the piston at any angle.

In some instances the features of the present invention are desirably obtained by employing an orifice which is in effect the main valve opening when the mainvalve is only partially open. This is illustrated in the form of Figures Sand 6. In this form the valve 56 has a hollow interior coaxially with the valve and forms a cylinder 60'. There is a tail piece 64 extending from the valve through the seat. The'streamlining at 65 is here provided on the inlet edge of the seat, which in thiscase the upper edge since the inlet 51,-is at the right-hand end. 5

This overcomes the effect of pressure A piston 71 coaxial with the valve makes a free'slid'-' ing lit in the cylinder 6ll'. The piston engages stops 72 extending radially inward from the valve on the side of the piston remote from the seat, preventing the valve from fully closing so as to create a constantly open orifice 62' between the main valve and the seat in the position nearest to closing (never fully closed) which the valve attains. The orifice is thus a conical ring and the streamlining of the deflecting surfaces at the inlet mouth of the orifice conforms to the requirements for streamline flow as above set forth, the length of the orifice likewise conforming to the dimensions suggested above.

In order to adjust the orifice, the piston 71 is mounted on a threaded shank 7'3 threaded through the bonnet 55 and having a screw driver notch 74 at the outer end for adjustment. To prevent tampering and hold the adjust rhent the shank iscovered by a cap nut 75',

The pressure tap 66 in the form of Figures and 6 extends through the valve transversely to the flow of the stream and communicates with the control chamber 61. on the inside of the valve.

In operation in the form of Figures 5 and 6, the streamline how with metastable state occurs between themain valve and the seat in the, almost-closed position of Figure 5, and when the temperature of the condensate is low enough so as to maintain reduced pressure in the 7 to open;

It is'preferable to use a wholly separate orifice from the main valve passage, as shown in the form of Figures 7 and 8. In this form the cylinder 66' is constructed in the valve beyond the seat, and the orifice 62 extends radially inward through the valve 56 to a central passage 67 through the valve and tail piece connected to the outlet. The pressure tap 66 is transverse to the orifice as in the other forms and extends through the valve into the control chamber 61. An annular screen 76 suitably of wire mesh surrounds the inlet to the orifice 62 A suitable slot around the valve inside the strainer permits fluid to distribute to the orifice 62 The valve 56 of Figures '7 and 8 resembles that or" Figures 5 and 6 except for the location of the orifice, the provision of the strainer and the omission of the stops. This valve operates substantially the same as that of Figures 5 and 6 except that it is capable of fully closing. The position of the piston 71 is adjustable.

In some cases it is desirable to form the orifice in one or the other of the mating surfaces or" the main valve and valve seat. In the form of Figures 9 and 10 the orifice 62 is a slot or groove along the conical face 57 of the valve 56 the valve resembling the construction of Figures 1 to 4 without the extended tail piece. The valve is incapable of fully closing, since in the position of Figure 9 there is alway leakage through the orifice 62 The seat is streamlined at 65 so as to permit streamline flow. V

This form operates similarily to that of Figures 5 and 6, the pressure tap 66 extending transversely from the groove to the interior of the valve.

a In the form of Figures 12 to 14 inclusive the seat 545 is placed ofi center at the outlet side of the cylinder 69, and the valve 56 is a disc having the orifice 62 in the form of a slot from the inlet to the outlet side of the disc across the seat. The slot is streamlined as is also the valve seat at 65. The pressure tap 66 extends transversely to the slot through the disc to the pressure chamber 61'. 1 v

l The disc closely but freely fits the cylinder 6% and responds to the pressure in the control chamber. The

the center under the disc, cooperating with the adjacent: portion ofv the seat, and the disc is. free to turn without changing theresponse to vapor conditions in the. medium. flowing through the orifice.

' The clearance between'the disc and the cylinder permits some unavoidable leakage, but with reasonable fit this is a minor consideration, the control being in response to the pressure tap from the flow stream through the single orifice.

The control orifice will desirably be placed symmetrically around a tap tube as shown in the form of Figures 15 and 16. In this form a cylindrical valve 56 is provided with a strainer at 76 extending clear around the valve at a. point betweenthe conical surface 57 and the piston 58. Transverse openings 77 behind the strainer extend into a central bore 64', which has streamlined approach annular curved surfaces 65 in a shoulder portion 78 at the center. A tap tube 81} is mounted in a tubular nut 81 threaded in the top of the valve, and the tap tube extends in spaced relation into the bore 64 to form a control orifice 62 around the bore.

In the preferred embodiment of Figures 15 and 16,

the tap tube has pressure tap openings 66 extending radially inwardly into the bore 82 on the inside of the tap tube, and is closed at the bottom end. The tap tube is open at the top.

Various forms of construction of the tap tube may be used as. shown in Figures 17 to 170. In Figure 17 the lower closed end of the tap tube is rounded at 83 instead of being conical as at 84 in Figures 15 and 16.

The forms of Figures 17a to 170 have the advantage of reducing machining costs. In the form of Figure 17a the tap tube is open and has axial V notches 66 extending from the lower end toward the upper end and located below the entrance to the control orifice. In the form of Figure 17b the tap tube 81 is constricted at 84 near the lower end to form a tap opening 66 at the center near the bottom inside the orifice.

. In the form of Fimire 170 the tap tube has a bottom end 'closedas at83 in Figure 17 and has a side slot 66 in the throat of the control orifice to act as a tap opening.

The operation of this device is similar to that of the earlier forms described.

' In some cases the mechanism is desirably inverted, as for example to minimize the danger of difiiculty from dirt, which otherwise might obstruct the tap opening. The form of Figures 18 and 19 is designed in this way, bearing a resemblance to Figures 1 to 4 and also Figures 5 and 6. i

In this case a valve 56 .is somewhat of the type shown in Figures: 5 and 6, but without the limiters 72. The control orifice 62 is located between the orifice ring 63 and the tail piece 64' which extends up through the orifice ring. The tap openings 66 extend radially in and con nect with the bore 67 which communicates with the chamber 61 which receives piston 71 adjustably mounted as in Figures 5 and 6. The piston has free clearance from the wall of the cylinder 60 inside the valve.

The invention is also applicable to forms in which the control chamber is connected to the valve by a flexible wall such as a diaphragm or bellows. This is illustrated in the form of Figures 20 to 25 inclusive, which is a modification of the form of Figures 12 to 14 inclusive. In this form a disc valve 56" cooperates with a seat 54 and has a control orifice 62 in this case located all center with respect to the axis'and comprising a slot extending radially along the bottom edge ofthe disc across the seat 54. The control pressure tap 66extencls transversely through the valve 56 into the space above the valve inside the bonnet 55. The valve in this case is sealed to the bonnet by a flexible diaphragm 85 which is conveniently anchored annularly at the outside at 86 by being screwed between the bonnet and the bonnet seat, being held down by a Washer 87 sealed by an O-ring 88.

Qn the-inside the diaphragm is conveniently anchored in'theform of Figures 20 to 25 by a jam washer 90 engaging an O-ring 91 at the inside and held in place by a nut 92 threaded on a tubular upper extension 93. of the valve. i

If desired the diaphragm 85 can be held in the center by a Washer 91' gripped by a spun over 94 of the annular upward extension 93' from the valve.

The diaphragm is flexible, and preferably heat resisting. An example of a suitable material is fiber glass cloth coated with polytetrafluorethylene (Teflon) or a heat-resisting synthetic rubber. This form has the advantage that there is no leakage from the control chamber around the disc. The control orifice in this form'can be made very small indeed to give the smallest control flow consistent with good results.

1 The invention is applicable to bellows-forms instead of diaphragms. Figures 27 and 28 illustrate such a construction, which resembles that of Figures 9 and 10 except that flow is in the opposite direction and a bellows is: employed. In this case a bellows 95, suitably of the beryllium copper or stainless steel type, is coaxially mounted on a support 96 which is adjustably threaded through the bonnet as in the construction of Figures 5 and 6. At the other end the bellows mounts the valve 56 which is of the tapered circular character'and has a control orifice slot 62 and a tap opening 66 transversely thereto extending to the bellows interior.

The operation of this form is similar to that of Figures 2010125, and resembles that of Figures 9 to 11.

--The form of Figures 27 and 28 may be modified to conform to that of Figures 7 and 8 as shown in Figures 29 and30; the construction, however, being reversed as to direction of flow. In this case the controlo'rifice, pressure tap opening and strainer are as in Figures 7 and 8, and the control chamber is efiectively inside the bellows The invention may also be applied to a disc type of valve mounted on a bellows, as shownin Figures 31 and 32. In this form there is a control orifice 62 similar to that used in Figures 20 to 25, which extends radially,-

I to tained'wliich might'rupture 105;and 106. i

The structure of Figures 33 and 34 may be employed with a bellows 95, which is secured to the lower end of tube 97 by anchorage 107 fastened by nut 108 to the The device of Figure 35 operates similarly to that of Figures 33 and 34.

The invention may be employed also with a double bellows 95 as shown in the form of Figures 36 and 37.

through the disc across the seat, and the control-pressure tap. 66 extends transversely thereto into the interior of theiibellows 95. The bellows mounts the valve 56 as in the form of Figures 27 and 28.

-.In this form as in all others in which the orifice is located radially between the valve and the seat, the orifice does not diverge and preferably converges with approach to the outer edge to a degree which will provide uniform cross section of the flow stream as it moves radially outwardly.

1 :Where thediap'hragm is incapable of standing up under the steam temperatures, it is preferable to use the diaphragm form of Figures 33 and 34. In this case the valve 56 resembles that of Figures 1 to 4 but is inverted, and the bore 67 is extended downwardly by threading a tube 97 into the valve and extending the tube insidela bonnet extension 98 to interconnect annularly at 100 with the inside of a diaphragm 85 whose outside is clamped at 101 by bolts 102 between a diaphragm housing103 on the bonnet extension 98 and a diaphragm housing cap 104. To provide support for the diaphragm in its. extreme limiting positions, the diaphragm housing and of freezing, the form of Figures 33 and 34 is not as desirable as the'forms of Figures 20 to 25 inclusive,

although'the form of Figures 20 to 25 inclusive exposes the. diaphragm to prolonged exposure to steam.

;, It will be evident that if pressure differentials are ob In this form the valve 56 has a conical sealing surface as in the form ofFigures 1 to 4 and the seat 54f has curved approach surfaces 65 on the lower portion. The control pressure tap 66 is transverse to the conical surface of the valve and communicates with the interior of the bellows one side of the bellows at the center being secured to the valve at 111 and the other side secured to the bonnet near the center of the bellows at 112. The valve on the lower end has a central circular opening 113 which receives a guiding limiter 114 which is mounted on a threaded plug 73' adjusted as in the form of Figures 5 and 6.

In operation of the form of Figures 36 and 37, the limiter is adjusted so that it prevents the valve from fully closing as shown in Figure 36, thus providing the con stantly open orifice 62 between the valve and the seat.

In the above description a number of diflerent embodiments of the invention have been illustrated, but it will be understood that numerous other forms embodying the principles of the invention can be produced as desired.

The device of the invention diflers fundamentally in operation from the prior art as embodied for example in Schott U.S. Patent No. 2,234,387 above referred to. Schott employs an abrupt change in cross-sectional area of his main' flow stream where control pressure takeofi occurs. This favors thermodynamic equilibrium. Schott describes this at page 2, column 1, line 5, where he says the pressure created being substantially thesaturation pressure." A similar statement appears at page 3, column 2, lines 5 to'l2.

sch ott employs an abrupt edge, which forms one of the walls of the orifice, with a sharp shoulder promoting turbulencehandthus equilibrium. Thus Schott uses hot condensate flow conditions through the restricted passage such that when the pressure along the flow stream drops to,.. vap or pressure, flashing occurs which maintains the pressurezat the control pressure tap location at the vapor pressure level. Schott employs radially outward flow between parallel surfaces which locates the orifice throat or restriction at-the sharp entrance and provides for a divergent condition as the flow continues outward. This construction creates the greatest velocity head and suppression of pressure head at the inner entrance and is. most favorable to immediate establishment of thermodynamic equilibrium of the fluid as indicated by Schottr In the device of the present invention, however, there are gradual streamlined acceleration of the fluid to the maximum throat velocity and minimum interference with the 'flow stream so that hot condensate does not flash at equilibrium but tends to remain liquid in a metastable condition until it passes through the orifice. This results in tap pressures which are considerably below the vapor pressure for thermodynamic equilibrium. Thus it is possibleto get lower control pressures on the condensate at all temperatures up to saturation as compared with the control pressures onsteam.

the streamline requirement as indicated in the several forms shown.

I 38 compares the'typicalconditions fortap up].

the diaphragm, the cliaphragrrr before rupture is engaged on and supported by the surface eration for the Schott device in comparison with the device of the invention.

This plots as the ordinate the pressure of the fluid discharging in p.s.i.g. against the temperature in degrees Fahrenheit. 7

Curve 115 is the vapor pressure curve corresponding to the control pressure forthe Schott device, and curve 116 is the typical control pressure curve for the device of the invention proportioned for example as in the form of Schott Figures 1 and 2, but constructed to conform with applicants device illustrated for example in Figures 12 to 14. The control pressure curves in Figure 38 are based on initial pressure on the control elements at 100 p.s'.i.g.

if it be assumed that the valve of Schott Figure 1 isinitially in the closed position and operating on saturated condensate at 100 p.s.i.g. pressure at the inlet, the vapor pressure in the control chamber to permit the valve to lift for discharge may be calculated. Since the ratio of the valve seat diameter to the piston diameter is about 6 to 11, the conditions for valve balance (assuming zero discharge pressure) may be written as:

6 2 -11 2, Where P is the initial pressure P is the chamber pressure for balance of the valve P in turn is equal to P the vapor pressure of the fiowing condensate. If We solve this equation We find that P,,=0.336P Then if P is 100 p.s.i.g., P,,=33.6 p.s.i.g.

Upon referring to the steam table's, we find the saturation temperature for 33.6 p.s.i.g. is 279 P. which is the temperature for valve lift. This is 59 F. below steam temperature and is too low for many drainage requirements. Under similar design conditions experimental easurements indicate that the device of the invention discharges at a temperature of 296 P. which is only 42 F. below steam temperature.

Line 117 on Figure 38 shows the approximate chamber pressure for valve balance in the form of Schott Figure 1..

If a similar comparison is made for the form of Schott Figures 5 and 6, it will be found that in the Schott device valve lift is promoted when the control pressure drops to approximately 55% of the initial pressure. In this case,- assuming 100 p.s.i.g. initial pressure, the Schott valve opens on condensate when the temperature drops to 302 F. or 36 below steam temperature. On the other hand, the device of the invention when similarly proportioned will discharge practically at steam temperature. In Figure 38 the line for chamber pressure for valve balance in Schott Figures 5 and 6 is illustrated in 118.

t should be noted that the margin of closing on steam in both cases is quite narrow and represents the limiting condition for trap operation in the device of the invention. Thus the device of the invention is capable of opening on condensate practically up to steam temperature while the Schott device is limited to opening on condensate at appromately 36 below steam temperature with an initial pressure of 100 p.s.-i.g.

The above analysis is based upon the assumption that the valve of the invention is initially in the closed position with hot condensate flowing through a constricted passage. It should be realized that once the valve is open, the flow reaction on the valve will keep the valve open to considerably higher condensate temperatures, possibly up to steam temperature, and may cause independent continuation of operation on change of phase between condensate and steam. In practice, however, condensate flow will at least intermittently become established with the valve in the closed position and the difference in control pressure between the Schott device and the device of the invention results in a marked difference in performance, particularly if throttled flow becomes established. Thus it will be evident that according to: the

. l2 invention the device opens andcloses much closer to saturated steamtemperature than the devices of the prior art.

In the deice of the invention the streamlining reduces turbulence so that flashing .is far below the vapor pressure of the fluid, thus favoring trap operation.

By minimizing minute pressure fluctuations within the constricted stream due to turbulence, the liquid phase in the device of the invention remains in metastable condition to sub-vapor pressure levels necessary to overcome suriace tension forces which oppose initiation of change of phase, thus permitting desirable low control pressure. The device of the invention stabilizes the liquid phase at the control point along'the restricted flow passage at pres sures well below vapor pressure of the fluid to develop most favorable control pressure difiierential between the sub-saturated and the saturated liquid phase on the one hand, and the vapor'or gaseous phase on the other hand.

It should be realized in addition that the comparative advantages in performance are based on actual tests and that a closer approach to theoretical conditions will result in even greater advantages. if perfect metastability is realized with improved orifice form, with total suppression of flashing of the hot condensate, the tap pressure will approach the down-stream pressure, thus permitting -.valve lift and discharge for all condensate conditions.

Steam on the other hand will develop the critical pressure (between 50 and 60% of the initial absolute pressure) and will, therefore, provide a wide margin for valve closure. It is expected that these further optimum advantages will be more closely realized with closer attention to improved orifice form and surface smoothness. The lower dotted line 116 of Figure 38 shows this theoretically attainable limit.-

The device of the invention permits maximum control pressures on vapor and lower control pressures on all conditions of liquid. The device of the Schott patent however develops highest control pressure in condensate at near the steam temperature and a lower control pressure for sub-cooled condensate and for steam. Thus the Schott device at 'p.s.i.g. operates at 306 F. which is 32 below the steam temperature and' is the highest opening temperature on condensate which is consistent with closing on steam. The Schott device will not open on condensate until well below the steam temperature. The reversal of flow in the. device of the present inventor as compared with the Schott patent device has the follow ing advantages: 7

(1) In the piston device flow is always toward the bmair stream, so that there is little possibility of clogging y 1rt.

(2) Leakage around the piston is above the main flow stream, so as to protect from dirt.

('3) Control flow into the main stream is more favorable to maintenance of streamlined flow.

(4) The proportions of the parts are more favorable to a balanced design.

(5) Converging flow of the main stream favors streamlined conditionsin the orifice.

(6) Streamlining of the orifice is easier.

(7) In some, forms the device self drains and is less likely to encounter difficulty through freezing.

(8) Thevelocity impingement effect with the valve open issmall.

In view of my invention and disclosure variations and modifications to meet individual whim or particular need will doubtless become evident to others skilled in the art, to obtain all or part of the benefits of my invention without copying the method and apparatus shown, and I, therefore, claim all such insofar as they fall within the reasonablespirit and scope of my claims.

Having thus described my invention what I claim as new and desire to secure by Letters Patent is: 

